CN110546057B - Method for protecting a dual mass flywheel by detecting that the dual mass flywheel is in resonance while the engine is running - Google Patents
Method for protecting a dual mass flywheel by detecting that the dual mass flywheel is in resonance while the engine is running Download PDFInfo
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- CN110546057B CN110546057B CN201880025756.8A CN201880025756A CN110546057B CN 110546057 B CN110546057 B CN 110546057B CN 201880025756 A CN201880025756 A CN 201880025756A CN 110546057 B CN110546057 B CN 110546057B
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- 238000002347 injection Methods 0.000 claims abstract description 19
- 239000007924 injection Substances 0.000 claims abstract description 19
- 239000000446 fuel Substances 0.000 claims abstract description 16
- 238000001514 detection method Methods 0.000 claims abstract description 5
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/20—Reducing vibrations in the driveline
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/021—Introducing corrections for particular conditions exterior to the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0097—Electrical control of supply of combustible mixture or its constituents using means for generating speed signals
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/22—Safety or indicating devices for abnormal conditions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/32—Controlling fuel injection of the low pressure type
- F02D41/34—Controlling fuel injection of the low pressure type with means for controlling injection timing or duration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/1414—Masses driven by elastic elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/20—Reducing vibrations in the driveline
- B60W2030/206—Reducing vibrations in the driveline related or induced by the engine
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/06—Combustion engines, Gas turbines
- B60W2710/0616—Position of fuel or air injector
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
- F02D2200/101—Engine speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/28—Control for reducing torsional vibrations, e.g. at acceleration
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- General Engineering & Computer Science (AREA)
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- Transportation (AREA)
- Automation & Control Theory (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
A method for protecting a dual mass flywheel DVA by detecting that the DVA enters resonance when the engine is running, the DVA being disposed between an internal combustion engine and a gearbox of a vehicle, the method comprising the steps of: determining an average rotational speed of the crankshaft over time (Vsil) moy ) As a first parameter related to the risk of DVA coming into resonance, & measuring the maximum and minimum instantaneous rotational speeds of the crankshaft during said period of time, using the difference to define the maximum amplitude (Ampwn) of the crankshaft rotational fluctuation, as a second parameter related to the risk of DVA coming into resonance, & detecting that DVA has come into resonance during said period of time from a determined combination of values of said first and second parameters, & limiting or shutting off the injection of fuel into the cylinder after said detection.
Description
Technical Field
The present invention relates to a method and an apparatus for protecting a dual mass flywheel, which flywheel is arranged between an internal combustion engine and a gearbox of a vehicle, by detecting that the dual mass flywheel enters resonance when the engine is running.
Background
A dual mass flywheel DVA (or for the english version "Dual Mass Flywheel", DMF) is a flywheel consisting of two distinct parts, a first part connected to the engine and a second part connected to the gearbox of the vehicle via a propeller shaft. The two parts are free to rotate relative to each other and the degree of freedom of rotation is limited by a spring arranged between the two parts. The springs may mitigate the effects of each other, and more particularly, may reduce jounce in the transmission or variations in combustion engine speed caused by engine torque produced by the plurality of cylinders. Due to the presence of the springs, this dual mass flywheel design introduces resonant frequencies that may cause undamped movement of one part relative to the other, in extreme cases (if not with intervention) and may even damage the part.
Thus, a dual mass flywheel or DVA may enter resonance under certain operating conditions of the engine and vehicle. Experimental examples give the following results: the resonance frequency (converted to engine speed) is reached in the following cases:
for an engine speed of 300 tr/mn without engaged gear ratio,
for an engine speed of 400 tr/mn at Yu Yidang,
for an engine speed of 800 tr/mn in fifth gear,
engine speed of 1000 tr/mn for sixth gear.
Thus, the energy released by combustion increases the resonance amplitude without increasing the average velocity. Therefore, it is impossible to get rid of resonance by acceleration.
For example, document US20160153520 teaches a method for protecting a dual mass flywheel (DVA) of a vehicle based on comparing, by a controller, the vehicle engine speed with a threshold value set to avoid a resonance point of the DVA. If the engine speed is below the threshold, fuel injection into the engine is cut off by the controller to stop the engine. A fuel injection condition for restarting the engine is determined after fuel injection is cut off, and the controller monitors whether the condition is satisfied. If the fuel injection condition is reached, fuel injection into the engine is restarted by the controller to restart the engine.
According to document EP 2 230 393, the variation of the crankshaft rotation speed is compared with a determination of a threshold variation related to the driver behaviour in order to eliminate the resonance amplitude of the dual mass flywheel (DVA). The determination of the threshold variation in relation to the driver behavior is fixed based on an operating state reflecting the intention of the vehicle driver to accelerate or decelerate, and this operating state is given, for example, by an action on a brake pedal. Accordingly, the start of the resonance of the DVA can be correctly detected based on information about the intention of the driver of the vehicle (including whether or not a braking operation is performed). Thus, variations in power generated by the engine can be reduced or eliminated at the appropriate time.
Disclosure of Invention
The present invention proposes a method and apparatus for protecting a dual mass flywheel by improving the detection of the dual mass flywheel entering resonance and in particular by increasing the detection speed.
It is therefore an object of the present invention to propose a tool to enable limiting the time spent by a dual mass flywheel at resonance speed in terms of amplitude and duration.
Another object of the invention is to propose a tool that makes it possible to reduce the noise inside the vehicle.
Another object of the invention is to propose a tool that makes it possible to protect the transmission from variations in the speed of the crankshaft, which are caused by combustion in the cylinders.
Another object of the invention is to propose a tool that makes it possible to limit the disturbance to learning in the non-combustion deceleration phase by detecting the condition of DVA coming into resonance as early as possible.
More specifically, the invention relates to a method for protecting a dual mass flywheel or DVA by detecting the resonance of the dual mass flywheel when the engine is running, the flywheel being arranged between the internal combustion engine and the gearbox of a vehicle, characterized in that it comprises the steps of:
determining the average rotational speed of the crankshaft over a predetermined given period of time, as a first parameter concerning the risk of the dual mass flywheel coming into resonance,
measuring the maximum and minimum instantaneous rotational speeds of the crankshaft over said predetermined given period of time, using the difference to define the maximum amplitude of the crankshaft rotational fluctuation, as a second parameter related to the risk of the dual mass flywheel coming into resonance,
detecting that the dual mass flywheel has entered resonance in accordance with a determined combination of values of said first and second parameters within said predetermined given period of time,
after detecting that the dual mass flywheel has entered resonance, the injection of fuel into the cylinder is limited or cut off.
The protection method according to the invention enables a very fast, efficient and robust detection of the dual mass flywheel coming into resonance by monitoring an effective combination of engine parameters over a predetermined given period of time, the engine parameters being obtained from the average rotational speed of the crankshaft and the maximum amplitude of the crankshaft rotational fluctuations (and thus of the engine rotational speed) evaluated simultaneously or almost simultaneously, i.e. within the same determined given period of time. These parameters may be measured or determined using a sensor of a known type now present on all internal combustion engines, which is a crankshaft position sensor, controlled by an engine control unit that performs the calculations. For example, a particularly suitable sensor is a toothed sensor, which in particular comprises 60 teeth for one crank ring. With such a position sensor, the engine control unit calculates the instantaneous rotational speed of the crankshaft tooth by differentiating the angular position over a predetermined given period of time, and thereby generates an average speed. Thus, the present invention can be easily implemented at minimum cost by means of simple software installed in an engine control unit (or ECU) with which all internal combustion engines are also equipped, and does not require any hardware other than that already existing.
Once the entering resonance is detected according to the basic steps of the method according to the invention and the diagnosis is made as such, several successive solutions can be implemented under optimal conditions for protecting the dual mass flywheel and the transmission as a whole. For example, for non-hybrid vehicles, one solution for preventing this resonance phenomenon is to limit or shut off the injection of fuel, an operation that may be performed by the engine control unit using any known means. The result of the cut-off injection is a decrease in the average speed of the crankshaft and a fluctuation in the engine speed that stops almost immediately due to the absence of combustion in the cylinder. In the case of a hybrid engine, one possible addition to the method according to the invention is to start the electric motor to take over from the combustion engine. The spray is then still restricted or cut off, and:
the engine speed is maintained by means of an electric motor,
resonance no longer exists because it is stimulated by combustion.
According to an advantageous feature, said determined combination of values of said first and second parameters is defined as follows within said predetermined given period of time:
the average rotational speed of the crankshaft employs:
a value between a predetermined maximum increase value and a predetermined maximum decrease value, distributed on both sides of a stable average speed value, and
said stable average speed value being lower than or equal to a predetermined threshold value,
the maximum amplitude of the crankshaft rotation fluctuation takes a value higher than or equal to a predetermined threshold value.
The first parameter (which is the average rotational speed of the crankshaft) is the critical parameter for the dual mass flywheel to go into resonance, consisting in: on the one hand, the speed stabilizes or substantially stabilizes around a constant speed and, on the other hand, it is lower than or equal to a predetermined critical rotational speed threshold, such as idle speed. In combination with the first parameter, the second parameter is a critical parameter that exceeds a predetermined maximum amplitude threshold that depends not only on the parameters inherent to the DVA but also on the parameters of the engine and gearbox, while the dual mass flywheel goes into resonance. The threshold may be determined by calibrating each vehicle. Thus, if the average rotational speed of the crankshaft is stable or substantially stable but too low, and if the maximum amplitude of the fluctuation of the crankshaft is too large, as will be described in further detail in the exemplary embodiment of the present invention, the injection is limited or discontinued, especially on non-hybrid vehicles. No special intervention by the engine control unit is required in any other case, since no resonance is detected. The method according to the invention makes it possible in particular to exclude the case of a conventional engine start, as will be explained later in the description of exemplary embodiments of the invention.
According to an advantageous feature, said predetermined given period of time is comprised between 0.5s and 2s, preferably between 1s and 2 s.
This time period is a compromise which is long enough to detect a significant change in the average speed of the crankshaft, i.e. its stability in this case, and short enough to allow for example the engine control unit to take appropriate measures to interrupt the resonance as soon as possible from the moment the resonance is detected according to the method according to the invention.
The invention also relates to a device for protecting a dual mass flywheel or DVA by detecting the resonance of the dual mass flywheel when the engine is running, the flywheel being arranged between the internal combustion engine and the gearbox of a vehicle, characterized in that it comprises:
means for determining an average rotational speed of the crankshaft over time, over a predetermined given period of time, as a first parameter concerning the risk of the dual mass flywheel coming into resonance,
means for measuring the maximum and minimum instantaneous rotational speeds of the crankshaft over said predetermined given period of time, using the difference to define the maximum amplitude of the crankshaft rotational fluctuation, as a second parameter related to the risk of the dual mass flywheel coming into resonance,
means for detecting that the dual mass flywheel has entered resonance in accordance with a determined combination of values of said first and second parameters within said predetermined given period of time,
means for limiting or cutting off the injection of fuel into the cylinder after detecting that the dual mass flywheel has entered resonance.
According to an advantageous feature, said means for determining an average rotational speed of the crankshaft, said means for measuring a maximum and a minimum instantaneous rotational speed of the crankshaft, said means for defining a maximum amplitude of the rotational fluctuation of the crankshaft using the difference values, and said means for detecting that the dual mass flywheel has entered resonance in accordance with a determined combination of values of said first and second parameters within said predetermined given period of time, said means for limiting or shutting off the injection of fuel into the cylinder after detecting that the dual mass flywheel has entered resonance comprise a crankshaft position detector consisting of a plurality of teeth, such that the rotational speed of the crankshaft can be determined tooth by tooth; and an engine control unit.
Drawings
Fig. 1 is a graph of an example of a crankshaft rotational speed profile according to an example of a method according to the present invention, which protects a dual mass flywheel by detecting that the dual mass flywheel is coming into resonance while the engine is running,
fig. 2 is a flow chart of an example of a method according to the present invention, which protects a dual mass flywheel by detecting that the dual mass flywheel is coming into resonance while the engine is running,
figure 3 is a graph of an example of a crankshaft rotational speed profile during an engine start,
figure 4 is a graph of an example of a crankshaft rotational speed profile during return of the engine to idle,
fig. 5 is a schematic diagram of an exemplary embodiment of an apparatus according to the present invention.
Detailed Description
The graph in fig. 1 shows the evolution of a curve of the crankshaft speed Vvil or the vehicle engine speed measured over time, for example as the vehicle is driven by a multi-cylinder combustion engine. The abscissa axis carries a scale of time t in seconds(s), and the ordinate axis carries a scale of engine speed V or crankshaft rotational speed in revolutions per minute (tr/mn). Here, the idle speed is represented by a horizontal line defined at 800 tr/mn in a predetermined manner by an engine control unit (not shown).
In the engine example given in fig. 1, the crankshaft speed indicated by the curve Vvil changes over time from a rotational speed of about 2000tr/mn to an average rotational speed of about 500 to 600tr/mn over a period of about half a second (corresponding to half the length of the indicated abscissa axis), for example representing a sudden flameout phase or a decrease in the engine rotational speed in a low rotational speed region in which the vehicle is traveling at an extremely low speed with, for example, a fifth gear engaged.
The crankshaft speed profile Vvil is obtained by a toothed crankshaft position sensor comprising, for example, 60 teeth, so that the instantaneous speed of the crankshaft can be calculated in a known manner tooth by tooth, for example by measuring the angular displacement of the sensor between two signals given by the passage of two consecutive teeth from the sensor, and by measuring the time elapsed between these two signals. Thus, the speed profile shows the fluctuation of the engine speed over time over a predetermined given period of time, showing the acceleration of the speed during combustion in the cylinder and the deceleration between the combustions.
While measuring the instantaneous speed tooth by tooth using the sensor, the engine control unit also calculates the average rotational speed of the crankshaft by averaging the instantaneous speed over a predetermined given period of time in a known manner.
Thus, the curve Vsil shown in FIG. 1 has a first phase of reduction in the average rotational speed of the crankshaft from an average rotational speed of about 2000tr/mn to an average rotational speed of about 500 to 600tr/mn, i.e., below the average idle Vsil set at 800 tr/mn ral 。
By studying the rotation speed Vsil in FIG. 1 in the time period [0, t1 ]]The above variations, the average velocity was found to drop fairly sharply with a significant and increasing maximum fluctuation amplitude. According to the invention, since the average rotational speed drops sharply, there is no basis to detect that the DVA enters resonance, since the engine may be in a stop phase. Beginning at time t1 and including a period P lasting approximately 0.5s between times t1 and t2 as shown rés Above, it was found that the average speed calculated from the rotational speed Vvil of the crankshaft was stable or substantially stable (in this example, a rotational speed of about 500 to 600 tr/mn), and startedMaximum amplitude Amp of engine speed fluctuation Vvil Still large.
Here, "the average rotational speed of the crankshaft is substantially stable" means an average speed that may vary within a small allowable variation range around a stable rotational speed. Preferably, the allowable variation range of the average velocity is about 200tr/mn, more preferably about 100tr/mn.
Thus, according to the invention:
first, it is determined that the predetermined period of time P has elapsed rés An average rotational speed of the crankshaft, vsil, within (e.g., greater than 0.5s in FIG. 1, including between t1 and t 2) moy As a first parameter concerning the risk of the dual mass flywheel coming into resonance; advantageously, the average speed Vsil moy The method adopts the following steps:
-a value between a predetermined maximum increase value and a predetermined maximum decrease value, which value is distributed over a stable average speed value Vvil moy In this example, a steady average speed Vvil moy About 600tr/mn, with an allowable variation around the steady speed of, for example, about 100tr/mn, and
-said stable average speed value is lower than or equal to a predetermined threshold S Vvilmoyrés In this example, a threshold S Vvilmoyrés Average idle speed Vsil fixed at 800 tr/mn ral And an average speed Vsil stable over a period comprised between t1 and t2 moy Is about 600tr/mn,
second, it has been determined that the same predetermined given period of time P rés (i.e., including the period of time between t1 and t 2) the maximum and minimum instantaneous rotational speeds of the crankshaft, the difference being used to define the maximum amplitude Amp of the crankshaft rotational fluctuation Vvil As a second parameter concerning the risk of the dual mass flywheel coming into resonance; maximum amplitude Amp of crankshaft rotation fluctuation Vvil In this example, a value higher than or equal to a predetermined threshold S is employed AmpVvilrés For example, a maximum amplitude of greater than or equal to 100tr/mn, preferably greater than or equal to 200tr/mn,
at the predetermined given time period P rés In accordance with a certain combination of values of the first parameter and the second parameter, it is thus detected that the dual mass flywheel has entered resonance.
According to fig. 1, once a diagnosis of DVA entering resonance is made, the engine control unit can be used to limit or cut off the injection in any known way, so as to get rid of this resonance situation in the case of a non-hybrid vehicle.
An example of a method according to the invention will now be described using the flow chart of fig. 2.
To limit the use of the computing device and the memory space in the engine control unit, the activation of the method for detecting DVA entering resonance may advantageously be limited. For example, only when the engine is at a given average speed threshold Seuil survVvil The method can be activated only at the following runtime. The monitoring threshold Seuil survVvil The definition is as follows: exceeding the threshold Seuil survVvil There is no rotational speed at risk of DVA resonance. Threshold Seuil survVvil It may be established by calibration of each vehicle or is generally defined as a possible higher but more general rotational speed, e.g. around 2000 tr/mn.
In step 10 of FIG. 2, the engine control unit continuously calculates an average rotational speed Vsil of the crankshaft moy And when the average rotation speed of the crankshaft Vsil moy Below a set speed threshold Seuil survVvil (e.g., 2000 tr/mn) proceeds to the next step 20.
In steps 20 and 21 of fig. 2, the engine control unit continuously calculates the average rotational speeds Vvil of the crankshafts, respectively moy And maximum amplitude Amp of crankshaft rotational fluctuation Vvil 。
Critical steady average speed Vvil moy (i.e. lower than or equal to the speed threshold S Vvilmoyrés ) Depending on the engaged transmission gear ratios, and is thus established by calibrating each transmission ratio; if no gear is engaged, a critical stable average speed value Vsil moy For example about 600tr/mn (in the range comprised between 100 and 200 tr/mn).
Engine control unitHaving in memory the current period p= [ t1, t2]For example, a time period comprising a stability of between 0.5 and 2 seconds, preferably between 1 and 2 seconds, which is used as a basis for the calculation for detecting the DVA coming into resonance, at the end of which the control unit will continue to evaluate the first and second parameters (average rotational speed of the crankshaft Vvil moy And maximum amplitude Amp of crankshaft rotational fluctuation Vvil ) This involves the monitoring period indicated by step 22 in fig. 2.
In step 30, in the current period p= [ t1, t2]In that, the engine control unit monitors the evolution of the average speed as described above in order to detect its stability as also described above, and also to compare the value Vvil of this average rotational speed of the crankshaft moy And a speed threshold S Vvilmoyrés Compares and calculates the maximum amplitude Amp of the crank rotation fluctuation Vvil With a predetermined threshold S AmpVvilrés These operations are also performed in the memory of the ECU, and:
if the average rotational speed of the crankshaft Vsil moy Is stable or substantially stable and is also lower than or equal to the speed threshold S Vvilmoyrés And (2) and
if the calculated maximum amplitude Amp of the crankshaft rotation fluctuation Vvil Greater than or equal to a predetermined threshold S AmpVvilrés ，
Then in step 50 in fig. 2, the engine control unit limits or shuts off the injection of fuel into the cylinder; the method then returns to step 10 described above.
If the answer to step 30 is negative, the engine control unit proceeds to step 40 as follows:
if the average rotational speed of the crankshaft Vsil moy Is not stable or not substantially stable, or
If the average rotational speed of the crankshaft Vsil moy Above the speed threshold S Vvilmoyés Or (b)
If the calculated maximum amplitude Amp of the crankshaft rotation fluctuation Vvil Below a predetermined threshold S AmpVvilrés ，
Then in step 60, the engine control unit increases the torque to a torque limit demanded by the driver; the method then returns to step 10 described above.
If the answer to step 40 is negative, the method returns to step 10 described above.
Fig. 3 shows an example of the evolution of the rotational speed of the crankshaft during engine start-up, which fig. 3 must not lead to a diagnosis that the DVA has entered resonance, according to the method described in fig. 2, as will be explained later.
The abscissa and ordinate axes in this fig. 3 are the same as those of fig. 1, and the same reference numerals as those used in fig. 1 denote similar objects.
In the period p= [ t1, t2]In (2), the engine control unit records the average rotational speed of the crankshaft, vsil moy Subsequent to time t2, the average speed stabilizes around a rotational speed of about 800 tr/mn representing engine idle speed with attenuated crankshaft rotational fluctuations. Average rotational speed of crankshaft Vsil in period P moy Maximum amplitude Amp of crankshaft rotation fluctuation during abrupt increase Vvil Is high and exceeds, for example, a threshold S used in an engine control unit AmpVvilrés . However, the average speed Vsil in the period P moy The second parameter of the evolution composition of (c) does not show any stability. Thus, step 30 according to the flow chart of fig. 2 is not satisfied, and in this case the method proceeds to step 40, which is the opposite step to step 30.
In the example of fig. 3, step 40 is satisfied because, within the considered period P, although the maximum amplitude Amp Vvil Above threshold S AmpVvilrés But average speed Vvil during period P moy Is unstable, the second parameter being a substitute for the first parameter in step 40. Thus, in this case, the method proceeds to step 60, which includes increasing the engine torque within the torque limits requested by the driver.
Fig. 4 shows an example of the evolution of the rotational speed of the crankshaft during the return of the engine to idle, which fig. 4 does not necessarily lead to a diagnosis that the DVA has entered resonance, according to the method described in fig. 2, as will be explained later.
The abscissa and ordinate axes in fig. 4 are the same as those in fig. 1, and the same reference numerals as those used in fig. 1 denote similar objects.
During a period p= [ t1, t2 of time comprised between the times t1 and t2 shown]In (2), the engine control unit records the average rotational speed of the crankshaft, vsil moy Stability around a rotational speed of about 800 tr/mn representing engine idle speed, which is accompanied by a small amplitude Amp of engine rotational speed Vvil Is a fluctuation of (a). Although the average speed Vsil moy Is stable, but the engine control unit therefore records a lower than critical resonance threshold S for the same period of time P AmpVvilrés Maximum amplitude Amp of (a) Vvil . Thus, step 30 according to the flow chart of fig. 2 is not satisfied, and in this case the method proceeds to step 40.
In the example of fig. 4, step 40 is satisfied because, within the considered period P, the maximum amplitude Amp Vvil Below the threshold S AmpVvilrés . Thus, in this case, the method proceeds to step 60, which includes increasing the engine torque within the limits of the torque requested by the driver.
In fig. 4, before time t1 of entering period P, the engine control unit records a sharp drop in the average speed of the crankshaft accompanied by a high-amplitude fluctuation in the rotation of the crankshaft (as shown), and does not detect the entering resonance, because the average speed is not stable or not substantially stable, as explained in connection with the example of fig. 3.
Fig. 5 shows an example of a layout of an apparatus for protecting a dual mass flywheel, which is provided between an internal combustion engine 3 and a transmission 4 of a vehicle 5, by detecting that the dual mass flywheel enters resonance when the engine is running, the apparatus comprising:
means 1, 2 for determining the average rotational speed of the crankshaft over time, over a predetermined given period of time, as a second parameter concerning the risk of the dual mass flywheel coming into resonance, obtained from the crankshaft position sensor 1, and the engine control unit 2 processes the signal from the position sensor 1 in a known manner as described above,
means 1, 2 for measuring the maximum and minimum instantaneous rotational speeds of the crankshaft, using the difference to define the maximum amplitude of the crankshaft rotational fluctuation over a predetermined given period of time, as a first parameter concerning the risk of the dual mass flywheel DVA coming into resonance,
means 1, 2 for detecting that the dual mass flywheel has entered resonance in accordance with a determined combination of values of said first and second parameters within said predetermined given period of time,
means 2 for limiting or cutting off the injection of fuel into the cylinder after detecting that the dual mass flywheel has entered resonance.
As shown in fig. 5, the means for determining the average rotational speed of the crankshaft, the means for measuring the maximum and minimum instantaneous rotational speeds of the crankshaft, the means for defining the maximum amplitude of the rotational fluctuation of the crankshaft by means of the difference, and the means for detecting that the dual mass flywheel DVA has entered resonance in accordance with a determined combination of the values of said first and second parameters within a predetermined given period of time P, the means for limiting or shutting off the injection of fuel into the cylinder after the dual mass flywheel has entered resonance is detected comprising a crankshaft position detector 1 consisting of a plurality of teeth, so that the speed can be determined tooth by tooth; and an engine control unit 2 of a known type, for example typically equipped on a vehicle with an internal combustion engine and installed with software according to the method described above, for example with the aid of fig. 2.
Claims (5)
1. A method for protecting a dual mass flywheel (DVA), by detecting that the dual mass flywheel (DVA) enters resonance when the engine is running, the flywheel being arranged between an internal combustion engine (3) and a gearbox (4) of a vehicle (5), characterized in that the method comprises the steps of:
determining an average rotational speed of the crankshaft (Vvil) moy ) As involving dual mass flywheel ingressA first parameter of the risk of resonance is,
measuring the maximum and minimum instantaneous rotational speeds of the crankshaft over said predetermined given period of time (P), using the difference to define the maximum amplitude (Amp Vvil ) As a second parameter concerning the risk of the dual mass flywheel coming into resonance,
detecting that the dual mass flywheel has entered resonance in accordance with a determined combination of values of the first and second parameters over the predetermined given period of time, wherein the determined combination of values of the first and second parameters is defined as follows:
said average rotational speed of the crankshaft (Vvil moy ) The method adopts the following steps:
a value between a predetermined maximum increase value and a predetermined maximum decrease value, distributed on both sides of a stable average speed value, and
-said stable average speed value is lower than or equal to a predetermined threshold value (S Vvilmoyrés )，
Said maximum amplitude of the crankshaft rotation fluctuation (Amp Vvil ) With a value greater than or equal to a predetermined threshold (S AmpVvilrés ) Is used as a reference to the value of (a),
after detecting that the dual mass flywheel has entered resonance, the injection of fuel into the cylinder is limited or cut off.
2. The method according to claim 1, wherein the predetermined given period of time (P) is comprised between 0.5s and 2 s.
3. A method according to claim 2, wherein said predetermined given period of time (P) is comprised between 1s and 2 s.
4. An apparatus for protecting a dual mass flywheel (DVA) by detecting that the dual mass flywheel (DVA) is brought into resonance when the engine is running, the flywheel being arranged between an internal combustion engine (3) and a gearbox (4) of a vehicle (5), characterized in that the apparatus comprises:
for determining that the time is in advanceAverage rotational speed of the crankshaft over time (Vsil) over a given period of time moy ) Said average rotational speed being a first parameter related to the risk of the dual mass flywheel coming into resonance,
means (1, 2) for measuring the maximum and minimum instantaneous rotational speeds of the crankshaft during said predetermined given period of time (P), the difference being used to define the maximum amplitude (Amp Vvil ) Said maximum amplitude being a second parameter concerning the risk of the dual mass flywheel coming into resonance,
-means (1, 2) for detecting that the dual mass flywheel has entered resonance in accordance with a determined combination of values of the first and second parameters within the predetermined given period of time, wherein the determined combination of values of the first and second parameters within the predetermined given period of time is defined as follows:
said average rotational speed of the crankshaft (Vvil moy ) The method adopts the following steps:
a value between a predetermined maximum increase value and a predetermined maximum decrease value, distributed on both sides of a stable average speed value, and
-said stable average speed value is lower than or equal to a predetermined threshold value (S Vvilmoyrés )，
Said maximum amplitude of the crankshaft rotation fluctuation (Amp Vvil ) With a value greater than or equal to a predetermined threshold (S AmpVvilrés ) Is used as a reference to the value of (a),
means for limiting or cutting off the injection of fuel into the cylinder after detecting that the dual mass flywheel has entered resonance.
5. The apparatus according to claim 4, characterized by means for determining the average rotational speed (Vvil moy ) For measuring the maximum and minimum instantaneous rotational speeds of the crankshaft, using the difference to define the maximum amplitude (Amp) of the crankshaft rotational fluctuation Vvil ) And for detecting a dual mass flywheel according to a determined combination of values of the first and second parameters within the predetermined given period of time (P)(DVA) said means for entering resonance for limiting or shutting off injection of fuel into the cylinder after detection of the dual mass flywheel having entered resonance comprises a crankshaft position detector consisting of a plurality of teeth so that the rotational speed of the crankshaft can be determined tooth by tooth; and an engine control unit.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR1753336A FR3065256A1 (en) | 2017-04-18 | 2017-04-18 | METHOD FOR DETECTING THE ROTATING MOTOR OF A RESONANCE INPUT OF A DOUBLE DAMPER FLYWHEEL |
| FR1753336 | 2017-04-18 | ||
| PCT/FR2018/050866 WO2018193179A1 (en) | 2017-04-18 | 2018-04-06 | Method for protecting a dual mass flywheel, by detecting that it is entering into resonance when the engine is running |
Publications (2)
| Publication Number | Publication Date |
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| CN110546057A CN110546057A (en) | 2019-12-06 |
| CN110546057B true CN110546057B (en) | 2023-09-22 |
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| CN201880025756.8A Active CN110546057B (en) | 2017-04-18 | 2018-04-06 | Method for protecting a dual mass flywheel by detecting that the dual mass flywheel is in resonance while the engine is running |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US11203345B2 (en) |
| CN (1) | CN110546057B (en) |
| FR (2) | FR3065256A1 (en) |
| WO (1) | WO2018193179A1 (en) |
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| FR3103224B1 (en) * | 2019-11-20 | 2022-07-01 | Vitesco Tech Gmbh | Method for managing the injection of an internal combustion engine |
| CN111255583B (en) * | 2020-01-20 | 2021-05-11 | 东风汽车集团有限公司 | Protection control method and storage medium for dual-mass flywheel of engine |
| CN112761788B (en) * | 2021-01-13 | 2021-11-19 | 北京理工大学 | Diesel engine cylinder nonuniformity online detection method based on instantaneous rotation speed |
| CN113218664B (en) * | 2021-04-22 | 2023-03-21 | 东风柳州汽车有限公司 | Dual-mass flywheel resonance detection method, device, equipment and storage medium |
| CN114526156A (en) * | 2022-01-18 | 2022-05-24 | 东风汽车集团股份有限公司 | Dual mass flywheel device, vehicle, and control method for vehicle |
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Also Published As
| Publication number | Publication date |
|---|---|
| US11203345B2 (en) | 2021-12-21 |
| CN110546057A (en) | 2019-12-06 |
| FR3065257A1 (en) | 2018-10-19 |
| WO2018193179A1 (en) | 2018-10-25 |
| FR3065256A1 (en) | 2018-10-19 |
| FR3065257B1 (en) | 2019-04-12 |
| US20190375413A1 (en) | 2019-12-12 |
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